EP1024260B1 - Méthode de contrôle d'un turbocompresseur à géométrie variable dans un moteur diesel avec recirculation de gaz d'échappement - Google Patents

Méthode de contrôle d'un turbocompresseur à géométrie variable dans un moteur diesel avec recirculation de gaz d'échappement Download PDF

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Publication number
EP1024260B1
EP1024260B1 EP00300280A EP00300280A EP1024260B1 EP 1024260 B1 EP1024260 B1 EP 1024260B1 EP 00300280 A EP00300280 A EP 00300280A EP 00300280 A EP00300280 A EP 00300280A EP 1024260 B1 EP1024260 B1 EP 1024260B1
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Prior art keywords
vgt
engine
determining
indicative
value
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German (de)
English (en)
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EP1024260A3 (fr
EP1024260A2 (fr
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Liya V. Kolmanovsky
Michiel J. Van Nieuwstadt
Paul Eduard Moraal
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Ford Global Technologies LLC
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Ford Global Technologies LLC
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D41/0047—Controlling exhaust gas recirculation [EGR]
    • F02D41/0065—Specific aspects of external EGR control
    • F02D41/0072—Estimating, calculating or determining the EGR rate, amount or flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0002—Controlling intake air
    • F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/14—Introducing closed-loop corrections
    • F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
    • F02D41/1444—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases
    • F02D41/1446—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being exhaust temperatures
    • F02D41/1447—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being exhaust temperatures with determination means using an estimation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/14—Introducing closed-loop corrections
    • F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
    • F02D41/1444—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases
    • F02D41/1448—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being an exhaust gas pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/04—Engine intake system parameters
    • F02D2200/0402—Engine intake system parameters the parameter being determined by using a model of the engine intake or its components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
    • F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/40—Engine management systems

Definitions

  • This invention relates to turbocharged compression ignition engines having exhaust gas recirculation systems and, more particularly, to methods of controlling a variable geometry turbocharger (VGT) actuator position in diesel engines equipped with an exhaust gas recirculation (EGR) system.
  • VVT variable geometry turbocharger
  • EGR exhaust gas recirculation
  • High performance, high speed diesel engines are often equipped with turbochargers to increase power density over a wider engine operating range, and EGR systems to reduce the production of NOx emissions.
  • Turbochargers use a portion of the exhaust gas energy to increase the mass of the air charge delivered to the engine combustion chambers.
  • the larger mass of air can be burned with a larger quantity of fuel, thereby resulting in increased power and torque as compared to naturally aspirated engines.
  • a typical turbocharger consists of a compressor and turbine coupled by a common shaft.
  • the exhaust gas drives the turbine which drives the compressor which, in turn, compresses ambient air and directs it into the intake manifold.
  • VVT Variable geometry turbochargers
  • Document DE19728352A describes a VGT Control arrangement based on parameters including exhaust manifold pressure and mass flow of air intake (through compressor).
  • EGR systems are used to reduce NOx emissions by increasing the dilution fraction in the intake manifold.
  • EGR is typically accomplished with an EGR valve that connects the intake manifold and the exhaust manifold.
  • the recirculated exhaust gas acts as an inert gas, thus lowering the flame and in-cylinder gas temperature and, hence, decreasing the formation of NOx.
  • the recirculated exhaust gas displaces fresh air and reduces the air-to-fuel ratio of the in-cylinder mixture.
  • both the VGT and EGR regulate gas flow through the exhaust manifold and their effect is, therefore, jointly dependent upon the conditions in the exhaust manifold.
  • Excessive EGR rates displace the intake of fresh air and may lead to incomplete combustion of the injected fuel which, in turn, could cause visible levels of smoke to occur.
  • the actual flow through the EGR valve can vary greatly, even for a fixed EGR valve opening, due to exhaust pressure fluctuations generated by opening or closing the inlet guide vanes to the VGT.
  • VGT is used to regulate the mass airflow (MAF) and the EGR is used to regulate the intake manifold pressure (MAP).
  • MAF mass airflow
  • MAP intake manifold pressure
  • Figure 1 shows the steady-state values of compressor mass airflow rate (MAF) at an engine speed of 2000rpm, and a fuelling rate of 4.0 kg/hr.
  • Each line on the graph represents a constant EGR valve position wherein 0.0 is fully closed and 1.0 is fully open, and a varying VGT actuator position wherein 0.0 is fully closed and 1.0 is fully open.
  • opening the VGT increases MAF
  • a method of estimating the VGT actuator position in a compression ignition engine having an EGR system includes the steps of determining the exhaust manifold temperature (T 2 ), determining the mass flow rate (W 2 t ) through the turbocharger turbine, determining the exhaust manifold pressure ( p 2 ), determining the turbine back-pressure ( p exs ), and generating an VGT actuator position estimate ( ⁇ vgt ) as a function of W 2 t , T 2 , p 2 , and p exs .
  • the estimated VGT actuator position is then used generate an error term indicative of the difference between the estimated and desired VGT actuator position.
  • the error term can then be used to drive the VGT actuator to its desired position to regulate the intake manifold pressure.
  • the control system is advantageous in that it enables direct closed loop control of the VGT actuator position and/or turbine mass flow rate.
  • the control system thus has less sensitivity to VGT actuator imperfections or instabilities which may result from variable forces on the turbine guide vanes due to exhaust gas flow.
  • the estimator also allows for improved diagnostics of exhaust system problems such as restrictions due to a damaged muffler or deposits.
  • the method also allows for VGT actuator diagnostics. For example, a malfunctioning VGT actuator can be detected if a modified duty cycle signal is transmitted to the VGT actuator and the estimate of the VGT actuator position does not change.
  • An embodiment of the present invention provides an improved compression ignition engine control strategy. It dynamically estimates the VGT actuator position, turbine back-pressure, and exhaust manifold temperature using a reduced sensor set.
  • FIG. 1 there is shown a simplified schematic diagram of a compression ignition engine system 10 equipped with an exhaust gas recirculation (EGR) system 12 and a variable geometry turbocharger (VGT) 14.
  • EGR exhaust gas recirculation
  • VVT variable geometry turbocharger
  • a representative engine block 16 is shown having four combustion chambers 18.
  • Each of the combustion chambers 18 includes a direct-injection fuel injector 20.
  • the duty cycle of the fuel injectors 20 is determined by the engine control unit (ECU) 24 and transmitted along signal line 22. Air enters the combustion chambers 18 through the intake manifold 26, and combustion gases are exhausted through the exhaust manifold 28 in the direction of arrow 30.
  • ECU engine control unit
  • the engine is equipped with an EGR system 12.
  • the EGR system 12 comprises a conduit 32 connecting the exhaust manifold 28 to the intake manifold 26. This allows a portion of the exhaust gases to be circulated from the exhaust manifold 28 to the intake manifold 26 in the direction of arrow 31.
  • An EGR valve 34 regulates the amount of exhaust gas recirculated from the exhaust manifold 28.
  • the recirculated exhaust gas acts as an inert gas, thus lowering the flame and in-cylinder gas temperature and decreasing the formation of NOx.
  • the recirculated exhaust gas displaces fresh air and reduces the air-to-fuel ratio of the in-cylinder mixture.
  • the turbocharger 14 uses exhaust gas energy to increase the mass of the air charge delivered to the engine combustion chambers 18.
  • the exhaust gas flowing in the direction of arrow 30 drives the turbocharger 14. This larger mass of air can be burned with a larger quantity of fuel, resulting in more torque and power as compared to naturally aspirated, non-turbocharged engines.
  • the turbocharger 14 consists of a compressor 36 and a turbine 38 coupled by a common shaft 40.
  • the exhaust gas 30 drives the turbine 38 which drives the compressor 36 which, in turn, compresses ambient air 42 and directs it (arrow 43) into the intake manifold 26.
  • the VGT 14 can be modified as a function of engine speed during engine operation by varying the turbine flow area and the angle at which the exhaust gas 30 is directed at the turbine blades. This is accomplished by changing the angle of the inlet guide vanes 44 on the turbine 38.
  • All of the engine systems, including the EGR 12, VGT 14 and fuel injectors 20 are controlled by the ECU.
  • signal 46 from the ECU 24 regulates the EGR valve position
  • signal 48 regulates the position of the VGT guide vanes 44.
  • the command signals 46, 48 to the EGR 12 and VGT 14 actuators are calculated from measured variables and engine operating parameters by means of a control algorithm.
  • Sensors and calibratable lookup tables residing in ECU memory provide the ECU 24 with engine operating information.
  • MAP intake manifold pressure
  • EXMP exhaust manifold pressure
  • EXMP exhaust manifold pressure
  • an intake manifold temperature sensor 58 provides a signal 60 to the ECU 24 indicative of the intake manifold temperature.
  • a mass airflow (MAF) sensor 64 also provides a signal 66 indicative of the compressor mass airflow to the ECU 24.
  • Additional sensory inputs are also received by the ECU along signal line 62 such as engine coolant temperature, engine speed, and EGR valve position. Additional operator inputs 68 are received along signal 70 such as the accelerator pedal position or other fuelling request input.
  • p 1 refers to the intake manifold pressure in kPa.
  • Combined subscripts, such as "e2" refer to flows from the first to the second subsystem.
  • Figure 3 describes the logic routine to accomplish VGT actuator control based on intake and exhaust pressure, engine speed, compressor outlet temperature, engine coolant temperature and EGR valve position.
  • This logic routine resides in the ECU memory and is executed as part of the routine used to control the VGT actuator and EGR valve positions.
  • step 300 the engine intake flow (W 1e ( k )) is calculated as a function of the volumetric efficiency of the engine based on measured or estimated engine operating parameters.
  • the volumetric efficiency is stored in the ECU memory as a function of one or more of the following variables: engine speed, engine coolant temperature, fuelling rate, intake manifold pressure and exhaust manifold pressure.
  • T 1 is the intake manifold temperature which can be either measured from sensor 58 of Figure 2, or estimated based on the engine speed, fuelling rate and intake air charge temperature.
  • the values of the pumping constant k 1e can be derived as a function of measured or estimated engine parameters and used in the estimation of W 1e ( k ).
  • the value of W 1e ( k ) from step 300 is used to estimate the exhaust manifold temperature T 2 in step 302. This estimation is based on the principal that a portion of the energy released by combusting fuel, k 0 ( N )W f , is absorbed by the exhaust gas in the form of a temperature increase.
  • T 2 T 1 + k 0 ( N )W f /(W 1e c p )
  • the function k 0 ( N ) is determined from engine mapping data and T 1 can be either measured, estimated, or given a constant value. Embodiments where k 0 depends upon other variables are also possible.
  • the EGR flow W 21 ( k ) is estimated in step 304.
  • f 1 ( ⁇ egr ) represents the effective flow area of the EGR valve as a function of the position of the EGR valve. These values are stored as a lookup table in ECU memory.
  • R represents the difference between the pressure specific heat constant and volume specific heat constant
  • W 1e ( k ) and W f ( k ) can also be passed through first order linear filters with appropriate time constants.
  • step 308 the turbine flow W 2t is estimated from a recursive filter.
  • the density is expressed as: d(d 2 )/dt ⁇ (1/( s / ⁇ 2 +1)) (1/V 2 ) (-W 2t -W 21 +W e2 ) wherein s is the Laplace variable, ⁇ 2 is the filter time constant which is tunable, and V 2 represents the exhaust manifold volume.
  • the VGT actuator position is estimated in step 312.
  • the mass flow rate through the turbine is only weakly dependent on the turbocharger speed. This dependence is negligible and, therefore, not necessary to estimate the VGT actuator position.
  • the turbine effective flow area (A vgt ( ⁇ vgt )) is calculated from the modified orifice flow equation as follows:
  • a vgt ( ⁇ vgt ) W 2t (T 2 ) 1/2 / ( p 2 ⁇ ( p exs / p 2 ))
  • ⁇ (x) [(x- g +1) 2/ B - ( x-g +1) ( B +1)/ B ] 1/2 for x>PR c
  • ⁇ (x) [(PR c - g +1) 2/ B - (PR c - g +1) ( B +1)/ B ] 1/2 for x ⁇ PR c .
  • the parameters PR c , B , and g are regressed from turbine data supplied by the turbocharger manufacturer, or developed from data collected during engine mapping.
  • a map of the VGT effective flow area as a function of the VGT actuator position is stored in ECU memory.
  • Figure 4 graphs the estimated mass flow rate through the VGT turbine as a function of the pressure ratio across the turbine for various VGT actuator positions.
  • the actuator position ⁇ vgt varied from between 0.0 and 1.0 wherein 1.0 corresponds to the fully open position and 0.0 corresponds to the fully closed position.
  • lines 400, 402, 404, 406 and 408 represent VGT actuator positions 0.0, 0.25, 0.5, 0.75, and 1.0, respectively.
  • the VGT actuator position value can be used in any known manner regulate the turbine flow and, hence, MAP.
  • One such control method includes the steps of determining a desired VGT actuator position as a function of the engine speed and requested fuelling rate, and generating an error term indicative of the difference between the desired VGT actuator position and the estimated VGT actuator position. From the error term, a duty cycle for the VGT actuator can readily be determined and transmitted along signal line 48 of Figure 2 to drive the estimated VGT actuator to the desired value.
  • Any known controller can be used to drive the VGT actuator to the desired position, such as a proportional plus integral controller.
  • FIGS 5a-5c The performance of the novel estimation method for the VGT actuator position is shown in Figures 5a-5c.
  • Figure 5a plots the engine speed (line 500) in RPM for the fuelling rate steps of 5-6-7-5 kg/h shown in Figure 5b.
  • the resulting estimated VGT actuator position is shown in Figure 5c as line 504, and the measured VGT actuator position is shown as line 506.
  • the estimation method exhibits close tracking of the measured VGT actuator position.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Exhaust-Gas Circulating Devices (AREA)

Claims (10)

  1. Procédé d'estimation de la position d'actionneur d'un turbocompresseur à géométrie variable (VGT) (14) dans un moteur à allumage par compression comportant un système de recirculation des gaz d'échappement (EGR) (12) comprenant un clapet (34) reliant un collecteur d'admission (26) et un collecteur d'échappement (28) du moteur, ledit turbocompresseur VGT (14) comprenant un compresseur (36) relié à une turbine (38) comportant une aube de guidage d'entrée ajustable (44) sensible à un signal d'actionneur de turbocompresseur VGT, le compresseur (36) étant en communication avec le collecteur d'admission (26) et l'aube de guidage de turbine (44) étant en communication avec le collecteur d'échappement (28), le procédé comprenant les étapes consistant à :
    déterminer une valeur de température (T2) indicative de la température de collecteur d'échappement,
    déterminer une valeur de débit de turbine (W2t) indicative du débit massique à travers la turbine de turbocompresseur,
    déterminer une valeur de pression (p2) indicative de la pression du collecteur d'échappement,
    déterminer la valeur de contre-pression (pexs) indicative de la contre-pression de turbine, et
    générer une estimation de position de l'actionneur de turbocompresseur (αvgt) en fonction de W2t, T2, p2 et pexs .
  2. Procédé selon la revendication 1, dans lequel l'étape consistant à déterminer une valeur de température (T2) comprend les étapes consistant à :
    déterminer une valeur de température d'admission (T1),
    déterminer une valeur de débit d'admission (W1e) indicative du débit d'admission du moteur, et
    estimer la température d'échappement (T2) conformément à l'équation suivante : T2 = T1 + k0(N)Wf/(W1ecp)    où k0(N) représente l'énergie libérée par la combustion du carburant en fonction du régime du moteur (N), Wf représente le taux d'alimentation en carburant, et cp représente la constante de chaleur massique et de pression pour l'air à 300 K.
  3. Procédé selon la revendication 2, dans lequel ladite étape de détermination d'une valeur de température d'admission (T1) comprend l'étape consistant à mesurer la température du collecteur d'entrée à partir d'un capteur de température.
  4. Procédé selon la revendication 1, dans lequel l'étape de détermination d'une valeur de débit de turbine (W2t) comprend les étapes consistant à :
    déterminer une valeur de débit d'admission (W1e) indicative du débit d'admission du moteur, et
    déterminer une valeur de débit de recirculation EGR (W21) indicative du débit à travers le clapet pour EGR,
    déterminer une valeur de débit d'échappement (We2) indicative du débit d'échappement depuis le moteur vers le collecteur d'échappement en fonction de W1e et du taux d'alimentation en carburant du moteur (Wf), et
    estimer W2t en fonction de W21 et We2.
  5. Procédé de commande du débit d'air dans un moteur à allumage par compression comportant un système de recirculation des gaz d'échappement (EGR) comprenant un clapet reliant un collecteur d'admission et un collecteur d'échappement du moteur, et un turbocompresseur à géométrie variable (VGT) comprenant un compresseur relié à une turbine comportant une aube de guidage d'entrée ajustable sensible à un signal d'actionneur de turbocompresseur VGT, le compresseur étant en communication avec le collecteur d'admission et l'aube de guidage de turbine étant en communication avec le collecteur d'échappement, le procédé comprenant les étapes consistant à :
    déterminer une valeur de température (T2) indicative de la température du collecteur d'échappement,
    déterminer une valeur de débit de turbine (W2t) indicative du débit massique à travers la turbine de turbocompresseur,
    déterminer une valeur de pression (p2) indicative de la pression du collecteur d'échappement,
    déterminer une valeur de contre-pression (pexs) indicative de la contre-pression de turbine,
    générer une estimation de position d'actionneur de turbocompresseur VGT (αvgt) en fonction de W2t, T2, p2, et pexs,
    récupérer une valeur de position d'aube de guidage d'entrée de turbocompresseur VGT souhaitée (αvgt *) à partir d'une table de valeurs indexées par le régime du moteur et le taux d'alimentation en carburant,
    générer une commande de position d'actionneur de turbocompresseur VGT (Uvgt) en fonction de la différence entre les valeurs de position d'actionneur de turbocompresseur VGT souhaitées et estimées, et
    appliquer Uvgt à l'aube de guidage de turbine afin d'entraíner l'aube de guidage d'entrée vers les valeurs souhaitées respectives.
  6. Procédé selon la revendication 5, dans lequel l'étape de détermination d'une valeur de température (T2) comprend les étapes consistant à :
    déterminer une valeur de température d'admission (T1),
    déterminer une valeur de débit d'admission (W1e) indicative du débit d'admission du moteur, et
    estimer la température d'échappement (T2) conformément à l'équation suivante : T2 = T1 + k0(N)Wf/(W1ecp)    où k0(N) représente l'énergie libérée par la combustion du carburant en fonction du régime du moteur (N), Wf représente le taux d'alimentation en carburant, et cp représente la constante de chaleur massique et de pression pour l'air à 300 K.
  7. Procédé selon la revendication 5, dans lequel l'étape de détermination d'une valeur de débit de turbine (W2t) comprend les étapes consistant à :
    déterminer une valeur de débit d'admission (W1e) indicative du débit d'admission du moteur, et
    déterminer une valeur de débit de recirculation EGR (W21) indicative du débit à travers le clapet pour EGR,
    déterminer une valeur de débit d'échappement (We2) indicative du débit d'échappement depuis le moteur vers le collecteur d'échappement en fonction de W1e et du taux d'alimentation en carburant du moteur (Wf), et
    estimer W2t en fonction de W21 et We2.
  8. Dans un système de moteur à allumage par compression comportant un passage de recirculation des gaz d'échappement (EGR) (32) comprenant un clapet pour EGR (34) reliant un collecteur d'admission (26) et un collecteur d'échappement (28) du moteur, et un turbocompresseur à géométrie variable (VGT) (14) comprenant un compresseur (36) relié à une turbine (38), ladite turbine comprenant une aube de guidage d'entrée ajustable (44), le compresseur (36) étant en communication avec le collecteur d'admission (26) et l'aube de guidage (44) étant en communication avec le collecteur d'échappement (28), ladite aube de guidage (44) étant sensible à un signal d'actionneur de turbocompresseur VGT destiné à réguler la pression du collecteur d'admission, l'unité de commande de moteur destinée à réguler le débit d'air dans ledit moteur, ladite unité de commande de moteur (24) comprenant :
    une mémoire destinée à mémoriser une cartographie de rendement volumétrique de moteur en fonction des paramètres de fonctionnement du moteur, une cartographie de la surface d'écoulement efficace du clapet pour EGR en fonction de ladite position du clapet pour EGR, et une cartographie de la surface d'écoulement efficace de turbocompresseur VGT en fonction de la position d'aube de guidage de turbocompresseur VGT, et
    un contrôleur de contre-réaction destiné à générer ledit signal d'actionneur de turbocompresseur VGT, ledit contrôleur de contre-réaction étant programmé pour :
    déterminer une valeur de température (T2) indicative de la température de collecteur d'échappement,
    déterminer une valeur de débit de turbine (W2t) indicative du débit massique à travers la turbine de turbocompresseur,
    déterminer une valeur de pression (p2) indicative de la pression du collecteur d'échappement,
    déterminer la valeur de contre-pression (pexs) indicative de la contre-pression de turbine,
    générer une estimation de position de l'actionneur de turbocompresseur VGT (αvgt) en fonction de W2t, T2, p2 et pexs,
    récupérer une valeur de position d'aube de guidage d'entrée de turbocompresseur VGT souhaitée (αvgt *) à partir d'une table de valeurs indexées par le régime du moteur et le taux d'alimentation en carburant,
    générer une commande de position d'actionneur de turbocompresseur VGT (Uvgt) en fonction de la différence entre les valeurs de position d'actionneur de turbocompresseur VGT souhaitées et estimées, et
    transmettre Uvgt aux aubes de guidage de turbine afin d'entraíner l'aube de guidage d'entrée vers la valeur souhaitée respective.
  9. Unité de commande de moteur selon la revendication 8, dans laquelle ledit contrôleur de contre-réaction détermine une valeur de température (T2) en :
    déterminant une valeur de température d'admission (T1),
    déterminant une valeur de débit d'admission (W1e) indicative du débit d'admission du moteur, et
    estimant la température d'échappement (T2) conformément à l'équation suivante : T2 = T1 + k0(N)Wf/(W1ecp)    où k0(N) représente l'énergie libérée par la combustion du carburant en fonction du régime du moteur (N), Wf représente le taux d'alimentation en carburant, et cp représente la constante de chaleur massique et de pression pour de l'air à 300 K.
  10. Unité de commande de moteur selon la revendication 8, dans laquelle ledit contrôleur de contre-réaction détermine une valeur de débit de turbine (W2t) en :
    déterminant une valeur de débit d'admission (W1e) indicative du débit d'admission du moteur, et
    déterminant une valeur de débit de recirculation EGR (W21) indicative du débit à travers le clapet pour EGR,
    déterminant une valeur de débit d'échappement (We2) indicative du débit d'échappement depuis le moteur vers le collecteur d'échappement en fonction de W1e et du taux d'alimentation en carburant du moteur (Wf), et
    estimant W2t en fonction de W21 et We2.
EP00300280A 1999-01-26 2000-01-17 Méthode de contrôle d'un turbocompresseur à géométrie variable dans un moteur diesel avec recirculation de gaz d'échappement Expired - Fee Related EP1024260B1 (fr)

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US237634 1999-01-26
US09/237,634 US6067800A (en) 1999-01-26 1999-01-26 Control method for a variable geometry turbocharger in a diesel engine having exhaust gas recirculation

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